Winch



June 17, 1947.

J. H. WILSON WINCH Filed July 29, 1942 8 Sheets-Sheet l WINCH 1 8 Sheets-Sheet 2 Filed July 29, 1942 June 17, 1947. J H, w so 2,422,274

WINCH I Filed July 29, 1942 8 Sheets-Sheet 3 June 17, 1947.

J; H. WILSON WINCH Filed July 29; 1942 8 sheets sheet 4 June 17, 1947. J. H. WILSON WINCH Filed y 1942 llmunmmI,

June 17, 1947.

J. H. WILSON WI CH 8 shets sheet 8 Filed July 29, 1942 Patented June 17, 1 947 UNITED STATES PATENT OFFICE WINCH John Hart Wilson, Wichita Falls, Tex. Application July 29, 1942, Serial No. 452,773

5 Claims.

This invention relates to winches and more particularly to winches of the type primarily designed and constructed for use in drawing in orpaying out of cables of substantial length under conditions which result in widely fluctuating cable tension.

Numerous types of winches and winding and reeling devices have heretofore been designed and actually placed in use, for the accomplishment of widely varying tasks. In the usual case, however, the winch need only be designed to successfully raise and lower a vary greatly and to reel in and pay out a rope or cable which extends outwardly from the winch at an unvarying angle. The problems involved in the design of winches of this general type are relatively simple and a satisfactory design may be arrived at by conventional formulae.

Where the rope or cable which stretches from a winch to an object to be controlled or manipulated, however, is subject to rapid changes in the magnitude and direction of the pulling force which it must at all times resist, the problem of winch design becomes one of greater difliculty. This is particularly true in the case of the balloon winch, i. e., a winch the primary function of which is to manipulate a cable to the end Of which a captive balloon is secured. The captive balloon is frequently allowed to rise to a relatively great height and is, of course, of such character that it has no ability to resist rapid changes of position due to the action of air currents, the cable itself being the only element restraining the free movement of the balloon under the influence of such currents. Naturally, as the winds or air currents vary in direction, the balloon varies its angular or compass position with respect to the winch to which it is tethered and, necessarily also, the balloon must move downwardly when subjected to the action of a downwardly directed current of air. An upwardly directed current of air will tend to carry the balloon with it and impose a great strain upon the cable to which it is attached.

Under conditions of violent air turbulence, which not infrequently occur, the balloon may tend to change rapidly not only its compass position with respect to the'winch to which it is attached, but may be violently agitated vertically, alternately being driven downwardly and rising at relative1y high velocity. As a relatively light cable must be used in order that the balloon shall have the ability to rise to the desired height, it is clear that a problem of real difliculty in winch construction is presented. The cable must be protected against sudden shock which, unless weight which does not cushioned in some manner, would cause it to immediately snap and hence the winch to which the lower end of the cable is secured must be provided with means which will quickly and automatically function when the cable tension threatens to suddenly increase to an excessive amount, to prevent damage. Manually operable means for controlling the cable under more normal conditions, is also necessarily provided it being clear that no completely automatic mechanism can be relied upon to properly manipulate the cable under all weather conditions and also apparent that the judgment of an operator must be exercised at all times in the control of a balloon winch in a combat zone. Likewise the cable, being of comparatively fragile type, may too quickly become frayed, and may break, unless the winch mechanism with which it comes in contact is designed in such manner as to prevent premature or excessive wear, to the greatest extent possible. One difiiculty heretofore commonly met with in the operation of balloon winches of previously known types has arisen in connection with the operation of the storage drum upon which the cable is wound, the cable having a tendency to wind unevenly and to pile up at the ends of the drum, greatly increasing the wear incident to winding and unwinding. Numerous other problems of design are peculiarly associated with the balloon winch and it is the general purpose of the present invention to provide an improved winch mechanism which is particularly suited for use as a means to which a balloon, such as'a barrage balloon, may be tethered and by means of which the movements of the balloon may be controlled in an improved manner at all times with minimum care on the part of the operator and minimum wear of both cable and winch mechanism.

In order that the possibility of cable breakage shall be rendered practically negligible, the improved winch is equipped with novel automatically acting mechanisms by means of which possible damage due to sudden variations in cable tension can be adequately taken care of. Means under the control of an operator is provided for adequately manipulating the cable quite regardless of the compass direction in Which the cable extends from the winch, this means including a novel cable guide which not only facilitates free swinging movement of the cable with respect to the winch, about a vertical axis, but also permits the angularity of the cable with respect to the horizontal to vary greatly, from a position in which the cable extends approximately vertically upwardly to a position in which it extends downwardly, except insofar as the angularity of the,

signed, transportable from point to point upon motorized equipment. It is furthermore so designed that the eiiiciency of the operator, who must remain on duty under the most adverse weather'c'o'nd tions and for long periods of time, is promoted, a seat being provided uponwhich the operator can position himself in such manner as to keep the balloon within his field of vision at all times with minimum physical discomfort, the several controls of the mechanism being so disposed as to be within the immediate reach of the operator when so positioned, thus facilitating proper and eflicient manipulation of the balloon with the expenditure of the least effort. The operators seat is constructed and adjustably mounted in a novel manner and likewise a protective canopy support is so arranged that it may be quickly adjusted to an operative position when the seat is moved to such position, and returned to inoperative position quite as readily when the seat is returned to its inoperative position. In their inoperative positions the seat and protective canopy are compactly disposed with respect to the supporting'frame and other elements of the winch, so that the entire winch occupies a minimum space for transportation. In their operative positions both chair and protecting canopy frame are extended so as to position the operator most advantageously for the work in hand. All cable contacting portions. of the which are designed and positioned so as to subject the cable to the least possible amount of bending, particularly about curves of short radius, and the spooling mechanism associated with the storage drum causes the laying on to the drum of successive layers of cable in such manner that these layers are continuous and smooth, all possibility of piling up of the cable being completely avoided.

The winch mechanism includes numerous additional improved details of design, which will hereafter be fully described. It may be said that certain features of the winch may be advantageously used in the construction of winches of other types although the primaryobje'ctive of the invention is to provide a special purpose winch of outstanding utility. Likewise the invention contemplates certain changes in the design and arrangement of its component elements, in adapting the winch for the accomplishment of tasks of somewhat different nature from that of balloon cable control. That form of the winch, therefore, which is illustrated in the accompanying drawings, is set forth by way of example only and it is contemplated that, without departure from the invention, various changes and rearrange'r'ne'nts of the various elements and subcombinations may, readily be effected.

In the drawing-s: v 7

Figure 1 is a schematic view in which are illustrated those elements of the winch mechanism which are actually contacted by the cable, the

manner in which the cable is threaded through the machine being readily perceptible;

Figure 2 is a top plan view of the winch, the operators seat and protective canopy support being shown in extended position;

Figure 3 is a side elevation of the winch;

Figure 4 is a section on line 4-4 of Figure 3;

Figure 5 is a section on line 5- 5 of Figure 4;

Figure 6 is a section on line 6-6 of Figure 5;

Figure 7 is a section on line 1-4 of Figure 3;

Figure 8 is a section on line 8-8 of Figure 3;

Figure 9 is a section on line 9-9 of Figure 8;

Figure 10 is a section on line lit-l9 of Figure 8;,

Figure 11 is a section on line i l--i l of Figure 8;,

Figure 12 is a section on line 42-4 2 of Figure 8; Figure 13 is a section on line I3-! 3 of Figure 2;

Figure 14 is a side elevation of portion of the machine as viewed from a point on the opposite side of the machine from that occupied by the observer who perceives the machine as it is illustrated in Figure 3;

Figure 15 is a fro t elevation of the mechanism shown in Figure 14;

Figure 15a is asection on line Ibo-45a of Figure l5;

Figure 16 is a side elevation of the c perators chair showing, by the use of full and dotted lines, the chair in two positions of adjustment;

Figure 17 is a rear elevation of the chair showing it, in dotted lines in inoperative position;

Figure 18 is an enlarged side view of a portion of the chair support;

Figure 19 is a section on line 19-49 of Figure 16-;

Figure 20 is a section through portion of the cable guide over which the cable first passes as it passes into the winch;

Figure 21 is a plan view of the portion of the cable guide shown in Figure 20;

Figure 22 is a section on line 22*22 of Figure 20;

Figure 23 isa schematic view of nism for braking certain operative parts of winch;

Figure 24 isa side elevation of the cable guide over which the cable first passes as it goes into the winch and with which it last contacts as it leaves the winch;

Figure 25 is a front elevation of the same, partly broken away;

Figure 26 is generally similar to Figure 24, but

the mechathe shows certain portions of the guide broken away Inasmuch as it is desirable to transport balloon winches from place to place under varying :conditions of warfare it is preferred that all of the essential elements of the winch be compactly arranged with respect to each other within a space which may be said to be based upon a horizontal rectangular area, preferably an elongated rectangular area of such length and width that the entire winch, including any supporting frame, may be placed in or on a truck body of no great size. The winch which comprises the subject matter of the present invention has been designed so that this is easily possi le, the various operating units being compactly arranged with respect to each other and disposed upon framewhich is generally indicated by the numeral Ill in Figures 2 and 3. The details of construction of frame It may be varied widely butadvantafull lines, in operative position, and in a rectangular geously' it may comprise side members I I the undersurfaces of which, at the ends thereof, are upwardly inclined to facilitate movement of the winch onto and? off of the truck body. Side frame members II will be suitably connected by bracing members so that the entire frame will comprise one rigid rectangular supporting means.

By reference to the schematic view, Figure 1, the relative relationships of the several principal functioning elements of the winch may be readily perceived. A power plant such as an internal combustion engine is diagrammatically illustrated at I2, this power plant or prime mover being located at one end of frame II. At the other end of frame H is a cable guide I3 through or over which the cable passes as it leaves the winch, a short length of that portion of the cable which extends from the winch to a balloon being indicated at C in Figures 1 and 3. Intermediate the prime mover I2 and the cable guide. I3 are positioned the various instrumentalities found essential for the adequate control and manipulation of the-cable. The first of these instrumentalities is indicated diagrammatically at I4, this being the shock absorber which includes a sheave I5 around which the cable passes and resilient means generally indicated at I6 for supporting the sheave I5 in such manner that it may move toward the cable guide I3 when the tension in the cable in creases sharply. It will be observed that, after the cable leaves the cable guide I3 it passes directly to and around the sheave I5, the sheaves I1 and IB shown being merely provided to deflect the cable laterally, the guide I3 being located centrally of the frame and the cushioning means I a being located to one side of the prime mover I2. For convenience that reach of the cable intermediate the guide I3 and the shock absorber I4 is indicated by the numeral C. After passing around the sheave I5 of the shock absorbing mechanism I I the cable passes forwardly to a traction device or surge drum generally indicated at T, that reach of the cable which extends between these two portions of the winch mechanism being indicated at C The traction device T is provided, comprising essentially two drums or multi-grooved sheaves I9 and 20, disposed one above the other and supported for rotation about parallel axes, the cable first passing beneath sheave I 9 and upwardly to and around sheave 29, then downwardly around sheave I9, and so on until it engages each sheave a plurality of times, the various wraps of the cable lying in spaced grooves formed in the cable receiving surfaces of the respective sheaves and the length of contact between the cable and the two sheaves being, in the aggregate, so great that slippage betwee the sheaves and cable may not occur, regardless of the magnitude of the tension exerted on the cable by the balloon attached thereto, and in particular regardless of the tension in the reach C of the cable. The sheave I9 is arranged to be driven in either direction of rotation by powe developed in the prime. mover I2 and transmitted by means to be later described, and the rotation of sheave may be opposed by braking means generally indicated at B so that, by means of the traction device T, the movements of the cable may be positively controlled, the operator, by manipulating suitable control elements, either driving sheave I9 (in either direction of rotation) or disconnecting this sheave from the power source and controlling the paying out of th cable by suitably manipulating the friction applying means B.

, From the lower sheave I9 of the traction device 6 T the cable passes forwardly to a level winding or spooling device generally indicated at. 8, passing over a guide sheave 2'2 and finally on: to a cable storage drum generally indicated at: D, that reach of the cable intermediate the traction device and the spooling mechanism being indicated at C this reach passing over two direction changing sheaves 23'- and 24', respectively, and that reach of the cable which lies intermediate the spooling device S and the storage drum D being indicated at C The storage drum D is driven by power derived from the prime mover I2 and in the normal operation of the winch the reach 0 of the cable will all times be maintained under tension, whether the cable is being drawn in or paid out but, by reason of the presence of fri'ctionally driven elements in the operative connection between the storage drum D and the prime mover the tension of reach (3* of the cable is maintained relatively low at all times, only suii'icient in magnitude to insurea tight wrap of the cable on the storage drum. Only that portion of the cable extending from the traction device '12 to the balloon will be under substantial tension and this tension is kept below a desired maximum at all times, to avoid cable breakage; The details of .the several instrumentalities which together comprise the winch will now be described.

The internal combustion engine diagrammaticaily illustrated at I2 may be of any type found to be suitable, and may even be replaced by an electric motor in localities where electric power is always available. Preferably, however, an internal combustion engine is employed and with it are associated a conventional clutch, located preferably within a housing indicated at 38, and a conventional change-speed gearing contained within housing 3 I, several speeds of forward drive being provided, and at least one speed of reverse rive, the direction of drive being controlled by the manipulation of a conventional hand lever such as indicated at 32. The drive shaft 33 of the prime mover projects toward the traction device T and has keyed to its outer end a hub 34 rotatably supported within the end wall of a housing (is rigidly supported by the" frame of the winch. Rotatably supported within an aligned apertur in the opposite end wall of the housing 35 is a generally similar hub 35, hubs 34 and 35 being connected by a flanged cylindrical coupling member 3? and circumferentially extending chains, of which portions are indicated. at 38. The arrangement is such that, by removing the chains 38, the engine shaft 33 may be disconnected from the power transmission mechanism by means of which the rotary motion of the shaft is communicated to the traction device and cable storage drum. This permits removal of the transmission from the unit, for the purpose of overhauling or replacement, quickly, easily and without disturbing the engine or traction device casing H.

The hub encircles and is non-rotatably se- Cured to short shaft 39 upon that end of which, remote from coupling 37, there is formed as an integral part the bevel pinion 46. Roller bearii' support shaft 36 for free rotation, these hearings supported in turn within apertures formed in member 52 which comprises a portion of the housing for the traction device driving mechanism, this housing being generally indicated at H. An extension 42' of memberllz has at its end a portion which extends transversely o i theaxisoi shaft 36, which portion is provided with a cylindrical aperture within which there is closely fitted the outer race of a roller bearing 43, this roller bearing supporting for free rotation the reduced end portion 39' of shaft 39, the pinion 48 being thus supported at both ends in antifriction bearings.

The teeth of the pinion 48 mesh with the teeth of a bevel gear 45 which gear is secured to a hub d6 keyed upon a shaft 4! disposed at right angles to the power shaft 33 and the pinion shaft 39 and extending horizontally, with its outer end projecting without the housing If and supporting a Windlass 49, commonly called a cathead. Shaft 41 is supported, intermediate the hub 43' of the Windlass and the bevel gear 45 by spaced roller or ball bearings indicated at 58 and an oil retaining ring and washer are indicated at and 52, respectively. It is clear that, when the motor shaft 33 is driven, the Windlass 49 will be revolved and that the direction of rotation of the windlass depends upon the direction of rotation of the shaft 33; The Windlass 49 is of general utility and may be utilized whenever the cable or rope is to be utilized in pulling, in the ordinary manner. In axial alignment with shaft 4-1 is a shaft 53. Shaft 53 is coaxial with and rigidly secured to the lower sheave l9 of the traction device T.

Generally, in the operation of the winch, the aligned shafts i! and 53 are coupled together for simultaneous rotation by means of a jaw clutch,

the longitudinally sliding member of which is indicated at 54 and the longitudinally fixed member of which is indicated at 55. Slide clutch member 55 is splined to shaft 53 in the customary manner and may be moved longitudinally upon this shaft by means of a shifter yoke of ordinary construction, portion of which is indicated at 56 and which is rigid with a horizontally extending rock shaft 5'? supported in a bearing mounted on the wall of housing H and to the exposed outer end of which there is rigidly affixed the operating lever 58. By moving lever 58 transversely of the machine, thus rocking shaft 51, the shifter yoke 56 may be caused to engage the jaw clutch elementslor to effect their separation as may be desired. It will be observed that the reduced end portion 53 of shaft 53 is supported in a bearing 55 located in a cylindrical recess formed within the hub G3, the two shafts 53, 41 being thus maintained in alignment at all times.

An anti-friction bearing of relatively large size is indicated at 38, this bearing supporting shaft 53 where it passes through the end of housing H. Keyed upon shaft 53 is the hub 6| of a double sprocket, the larger sprocket 52 being positioned directlyv below a similar sprocket 63 keyed upon shaft 64 upon the outer end of which the upper sheave 28 of the traction device is rigidly mounted. The axis of shaft 64 is parallel to the axis of the lower shaft 53 and the shafts are interconnected for simultaneous movement by means of a chain 85 which passes over and operatively connects sprockets 82 and 63.

multaneously, in the same direction of rotation, and at equal angular velocities when shaft 53 is operatively connected to the prime mover. Antifriction bearings 68 and 81 of rugged nature support shaft 84 for free rotation.

' In Figure 4 sheaves I9 and 28 of the traction device are illustrated in elevation, the cable receiving grooves beingclearly shown.

vided with a plurality of grooves, six grooves being The shafts 53 and 64 must, therefore, necessarily rotate si- 7 Each cable receiving surface of each of these sheaves is proprovided upon the thread oreceivingicylindrical face of the lower sheave and five grooves upon the face of the upper sheave or drum. The number of grooves may be varied as may be'found necessary'in the handling of cables'having different characteriscs and the sheaves of the grooves may be varied if desired to bring about increased or decreased intensity of frictionalengagement between cable and sheave. In any event, however, the cable receiving surfaces of the sheaves of the traction device or surge drum are so designed that, with the cable wrapped about these surfaces a desired number of times, slipping of the vcable circumferentially of the sheaves becomes impossible so long as the reaches of the cable passing to and from the traction device, respectively, are in tension. The traction device, therefore, is an instrumentality for positively pulling in or paying out the cable, although the engagement of the cable with the traction device is not positive, but is frictional only.

The cable storage drum D is in advance of the traction device T and is supported for rotation about an axis parallel to the shafts 53 and 84 of the traction device T, previously'referred to. The storage drum supporting shaft is indicated at 88, on end of this shaft being mounted 'in a bearing 33 fixed upon a pedestal 18 and the other 1 end being supported in an anti-friction bearing 12 mounted in the inner wall of a forward extension H of the housing H which encloses the shafts and driving gear of the traction device. The cable receiving cylindrical portion of the drum is indicated at '13 and its disc-like endsiat Hand "i5, respectively, the end 14 being provided'with a central aperture through which shaft 68 passes, an annular anti-friction bearing 15 encircling the shaft at this point and being snugly housed within the hub-like central portion of member 14. The ann'ular end 15 of the drum is provided with a similar hub-like portion 11 encircling shaft 38, and which also houses an anti-friction bearing, this bearing being indicated at T9. 7

The storage drum is, therefore, freely rotatable upon shaft 88 insofar as the drum supporting means just described is concerned. It is, however, frictionally connected to'the' shaft 68 so as to tend to rotate therewith at all times and this frictional connection maybe 'most clearly per ceived from an inspection/of Figures 8 and 9.

Disposed in a plane parallelto'the outer face of the end 15 of the drum, and so as tobe concentric with the axis of shaft 68, is an annular member or face 82 of friction material, such as may be used in theconventional automotive disc type clutch, and spaced slightly away from the an nular member 82 is a second similar member 83 positioned to engage the inner face of a member as formed as an annular plate concentric with'the axis of shaft 88. Member 84 is provided with a plurality of perforations through each of which projects a rigid pin 85 the inner end of eachof which is received and securely held within a cyl indrical aperture formed in the end '15 of the storage drum. 'Annular member 84is freelyslidable upon its supporting pins 85 and resilient.

means is provided, comprising a coil spring 88 encircling each pin 85, and an abutment nut 81 having 'a threaded connection-with the outer end b keyed or splined upon shaft 88, and to which disc the annular friction;member's 82 and 83 are secured, is interposed between the drum and.

annular plate 84. ;;Disc 881s formed in two halfportions to facilitate its assembly, and removal for replacement purposes. The members 82 and 83 are constantly clamped between the drum and plate 84, the degree of frictional-engagement between the several parts depending upon the intensities of the forces exerted bythe compression springs 86.

It will be observed that each pfthe threaded abutment members Bl is provided with an integral sprocket 8?! and a single sprocket cha n 9.9 passes over all of these sprockets as clearly illus-- trated in Figure -9,. At least the ,outerend of each spring abutment nut '81 is pol gonal and adapted to receive a wrench by means of which it may he rotated to increase or decrease the pressure cf the ass ciated sprin p n the annular member 84.. Naturally, by reason ofthe facttihat the :several abutment nuts 81 are interconnected by-the chain 9!) the adjustment of onenut willresult in the simultaneous adjustment of all othersso that the degree of friction between the friction disc 88 and the friction members 82 and ,813 may z-be varied at any time, quickly and easily and with assurance that the springs will continue at all times to act with equal pressures a ainst the clutch member 84.

ilfhe storage drum shaft 6.8 is driven by power from the prime mover, taken from the shaftfid of the traction device T, hubs l which is keyed to that shaft having :formed thereon a second sprocket 9i which is voperatively connected by means of a chain 9.2 :to a sprocket 93 which is integral with a sleeve :94 encircling that end of the drum shaft ;68 which lies within theextension H of the housing H. Anti-friction annular bearings intermediate shaft '68 and sleeve .594 are indicated at 95 and -91, respectively, bearing "916 being of conventional type, but bearing 9i having an elongated sleevedike inner race ill", the outer surface of which is provided with a plurality of inclined faces, as shown in Figure =11, each such face having associated therewith a roller 598 which at all times lies between that faceand the encircling cylindrical inner face of sleeve 94. The parts just described, i. e., the sleeve 9''! with its inclined faces, the rollers '98, and the cylindrical inner face of the outer sleeve 94, together comprise an overrunning or one-way clutch the effect of which is to clutch or couple together the sleeve 94 and the shaft 68 when the sprocket 93 is driven in one direction by the chain ea, in winding in the cable, but to disconnect the drum shaft 68 and sleeve 94 when the drum shaft is stationary and sprocket 93 is driven in the opposite direction.

The bearings 69 previously referred to as providing a support for the opposite end of the drum shaft 63 are likewise formed so as to'incluele one anti-friction bearing which has a similarly extended inner race which forms the inner member of a one-way brake, shown in section in Figure 12. The one-way brake at this end of shaft 63, Which brake is generally indicated by the numeral I is, however, reversed as compared with the one-way or overrunning clutch at the opposite end of the shaft. It functions to hold the shaft 68 stationary when that shaft is completely disconnected from its driving means by reason of the functioning of the overrunning clutch within the sleeve 94, thus preventing rotation of the cable storage drum '!3 unless the pull of the cable in the unwinding direction is sufficiently great to overcome the frictional force developed between the friction members '82 and 83 and-the drum and drum increases.

plate :84. ,It is the function of the one-way brake tile, therefore, to prevent free rotation of the cable storage drum under the pull of the cable and to insure that the upward movement of the balloon to which the cable is attached .is never at any times, free orunopposed motion, eventhough the traction device itself may berevolving freely, those reaches of the cable mdicated by the letters 0 and C being maintained under tension at all times so that the wrapping frictional engagement of the cable on the traction device will always begmaintained.

The overrunning clutch at the opposite endof the shaft, which includes the rollers 98, automatically functions to operatively connect the driving chain :92 to the drum shaft 68 when the traction device is operated in the direction to wind in the cable onto'the storage drum. Whenthe traction deviceT is .in operation to draw in the cable the "drum shaft '68 will likewise be .in operation and will drive the drum through the friction device previously described. The cable receiving drum .13 is of relatively large diameter and will :tend'to move at a relatively high circumferential speed, having the effect of attempting to wind onto the drum a greater length of cable than the traction device'T .is capable .of winding in and paying out toward the storage drum. During the time, therefore, that the cable is thus being drawn in and is passing to the storagedrum there will be asubstantial amount of slip between the friction disc 88 and the friction members 82 and 83, the amount of slip increasing as the diameter of the package of cable on the storage When the initial'winding of cable is being placed on the drum the slip will preferably be about eight per cent, whereas when the drum is full the slippage may be as great as fifty per cent or even slightly more. By the mechanism described, however, the cable tension between the storage drum and the traction device may not only be maintained at all times, which is essential, but may be maintained withinpredetermined limits with considerable accuracy. The mechanism employed for accomplishing this is of rugged construction and of simple and inexpenivenature, easily repaired-when worn and acces sible for quick adjustment at all times} 'It is, of course, essential that manually operable braking means be provided in association with the traction device so that this device may be locked against movement when desired or frictionally retarded When paying out cable. Such braking means includes a brake drum H15 keyed upon the end of shaft 64 and a brake band of the external contracting type, indicated at I06. One end of this 'brake'band is fixed, being attached by a pin l0! to a rigid stationary bracket I08 while the other end of the band is attached by a pin -I 01! to the free end of the upwardly extending arm Ill) of a bell crank lever mounted for rocking movement upon an arbor Hi, the other arm of this "bell crank lever, indicated at H 2, being connected by a link H3 to one end of a bell crank lever l M pivotally supported upon the frame of the machine. The lower end of the bell crank H4 is pivotally connected to a short link H 6 extending longitudinally of the frame, link 116 having its opposite end pivoted to a cross rod :ll"1 which in turn is connected by a link H8 to the lower end of anarm [t9 the upper .end of which is rigidly-fixed upon rock shaft I20 extending transversely ofthe machine and the ends of which are rotatably supported in bearings mounted upon the side frame members; Connected to the end of rock shaft I20 is a brake pedal I2I placed so that the foot rest I22 thereof may be conveniently engaged by the foot of an operator.

To the opposite end of cross rod II'I there is pivotally connected the end of an elongated link I25 which extends forwardly and the opposite end of which is connected to the lower end of a bell crank lever I26 mounted for supported movement upon the frame by a pin I21. The free end of the other arm of the bell crank I26 has pivotally connected thereto the free end of a brake band I28 of the external contracting type which band encircles a cylindrical flange I integral with the head I5 of the cable storage drum 13, the opposite end of the brake band I28 being connected at I30 to a fixed bracket I3I, so as to be immovable. It will be apparent that, when pressure is applied upon the brake pedal I2I by the operator the link I I8 will be drawn to the right (Figure 2) thus drawing the cross rod Ill and the links H6 and I25. The brake bands I06 and I25 will be simultaneously contractedand retarding forces exerted which tend to stop both the traction deviceand the storage drum, the braking force applied to the traction device, however, being. very much greater than that applied to the storage drum by reason of the action of the cross rod II'I, which has a differential effect as will-be apparent, the point of application of the braking force to this cross link being much closer to the link I25 than tothelinkllfi.

For the convenience of the operator a hand lever I33 is provided, the lower end of this lever being fixed on the rock shaft III. Any convenient means may be associated with the end lever for looking it in position after it has been moved to brake applying position, such for in stance as a pawl and segment and by this means the traction device may be permanently locked against rotation when it is disconnected from the prime mover. The second pedal which is shown to be mounted upon the rock shaft I20, and which is indicated by the numeral I35 is a clutch operating lever, the hub I36 to which the lower end of the clutch pedal I35 is affixed, being freely rotatable upon rock shaft I20 and also being connected by an arm and' link] 31 to the clutch operating shaft I38. Any suitable type of clutch and clutch operating mechanism may be employed and by means of which the driving connection between the prime mover and the other mechanism of the winch may be readily established or broken.

The traction device T is provided with an automatically acting braking means in addition to the manually operable braking means which has been described, which automatically operating brake can be most clearly perceived in Figures 2, 4, 5, and 6. Supported upon the end of the upper shaft 64 of the traction device, beyond or outside of the brake druml05 .isa second; brake drum, I40 the cylindrical outer surface of which comprises a braking surface. The drum or wheel I40 has a hub portion I4Ila of relatively large diameter and intermediate the hub and shaft 64' arepositioned roller bearings MI and I42 and an overrunning or one-way clutch I43, the clutch'being disposed intermediate the bearings. The clutch details may be'con- 'ventional and its function is to positively con'- nect the;brake drum I40 to shaft 64 when'shaft '64 rotates in the direction in which it must necessarily rotate when cable is being payed out but to operatively disconnect the drum I40 an shaft 64 when the traction device is operating to draw in the cable. The outer cylindrical friction surface of drum I40 is engaged by a band I45 which almost completely encircles the one end of this band being securely attached to an anchoring member, which may conveniently be a bracket rigid with the frame of the winch and the other end being preferably attached to an operating member (not illustrated) by means of which the pressure of the band on the drum may be controlled. While the pressure of the band on the drum may be adjusted from time to time as may be desired it exerts, between adjustments, an even constant pressure on the drum which tends to prevent the drum from rotating. The arrangement is such that, when the traction device is drawing in cable drum I40 will be stationary, shaft 64 having been operatively disconnected from the drum by reason of the action of the overrunning clutch; As soon, however, as the shaft 64 begins to revolve in the opposite direction, i. e., as soon as the traction device moves in a direction which results in the paying out of cable, the overrunning clutch I42 becomes active to clutch the drum I40 to shaft 64 and the shaft is immediately retarded by the action of the brake band I45on the drum.

This braking action is, therefore, automatic and is effective in the event that, for any reason, a sudden tension created in the cable is not opposed sufficiently braking mechanism previously described. It furthermore considerably decreases the manual effort required in the manipulation of the manually operable brakes and renders the operation of the Winch considerably smoother than it otherwise would be, particularly when a captive balloon is being subjected to turbulent air currents. Likewise, if the operator is killed or injured, or is forced to leave while the apparatus is in full operation, this brake will restrain the balloon and prevent it from escaping, the brake being normally set.

As previously stated the winch'includes a novel form of spooling or level winding mechanism for insuring the proper lay of the cable on the storage drum as the cable is drawn in. This spooling device is most clearly illustrated in Figures l4 and 15 where it is shown to comprise essentially the large diameter sheave 22 which is supported for oscillation along a path immediately in advance of the storage drumand substantially parallel to the axis of the drum, the length of such path of movement being coextensive with the distance between the drum heads I4 and 15.

The cable guide or sheave 22 is rotatably mounted upon the upper end of a supporting rod I5I mounted for rocking movement upon a supporting bracket I52 rigid with the winch frame about an axis normal to a vertical plane which includes the storage drum axis. Tne guide sheave 24 previously referred to is'so positioned that the reach of cable which is indicated by the numeral C passes off of that sheave approximately at a point intersected by the prolonged axis, about. which the member I5I rocks so that the cable reach C at all times is disposed parallel to supporting member I5! regardlessof its inclination to the vertical. In the operation of the-spooling device the guide sheave22 will be moved from the position which is approximately indicated in dotted linesat 22a to the approximate position indicated in dotted lines at 221) (in Figures 11 and 15) by forces applied to the sheave support-- by the manually operable 13' ing member II by novel mechanism shown in Figures 14 and 15, and which is operatively eonnected'to member I5.I ashort distance above its point of pivotal attachment to the bracket 152..

Thismechanism includes the cam .4153 mounted upon the outer end of a shaft #54 disposed par-al l'el to the .axis about which member IEei rocks, shaft 154 being rotatably supported a sleeve I155 which is rigid with .a casing 156., this casing housing a worm wheel .65! to which the inner end of shaft i is secured and a worm I58 the teeth of which mesh with those of the worm wheel i157, Upon the end of the worm shaft I53 whichlies without the housing '55 is mounted a sprocket wheel I60 which is connected by means of a chain Ifil with a sprocket wheel 52 mounted upon and rotatable with the storage drum shaft 68. An idler sprocket I63 rotatably mounted upon a swinging bar I 54 engages the lower reach of the chain Hit and serves to maintain the chain tight at all times, bar I6 which supports sprocket I63 being pivotally attached at .its upper end to bracket '10 and its lower end being adjustably attached to a turn buckle I65 to an angle member Iii-I rigid with the winch. frame. It will be clear that the heart-shaped cam I53 will be revolved about the axis of rotation of its sup porting shaft I54 whenever the storage drum rotates and that the movements of the cam will be synchronized with those of the drum although, by reason of the speed reducing effect of the worm and worm wheel the cam will revolve at a considerably reduced angular velocity than that of the storage drum. Opposed cam followers are indicated at I69 and no these cam followers comprising rollers mounted for free rotation about the pins Iii-9a and Ilfia, pins I 69a and I'iila connecting the links HI and I12 which are, respectively, parallel to and on opposite sides of cam I53. Link III is a straight link and is ex-- tended so that its end lies directly opposite rocking support I5 I, being pivotally connected to that member by pivot element i'lit. Link H2 is centrally offset in an upward direction .as shown in order to bridge the cam shaft I54.

.A vertical link I13 has at .its lower end an aperture through which the outer end of pin 1269a extends and the link is likewise pivotally connected at its upper end to a bracket H4 so that it is free to swing in a plane parallel to the plane of the cam I53. As the cam I53 rotates one surface or the other will serve as a thrust surface, applying a force to either the cam follower IE9 or the cam follower I10 and thus effecting annular rocking movement of the support 1.5I for the cable guide I50. As the sheave 22 reaches the end of its stroke the peak of the cam I53 passes the cam follower against which the cam has been active and movement of the rope guide 22 in the reverse direction is immediately commenced. By reason of the fact that that cam is shaped as shown there is no appreciable dwell of the rope guide 22 at the point where it reverses its move and hence piling up of cable at the ends of the drum, a difiiculty commonly met with in prior winches of this general class. It is, of course, important that, at the instant of reversal, lost motion in .the operating mechanism may not result in the undesirable dwell and it is, therefore, essential that the two cam followers be in close contact with the periphery I of the cam at the instant of reversal, when one follower becomes inactive and the other becomes active.

The possibility of lost motion is eliminated 'in the mechanism described, the cam follower sup- 14. porting means including the links 1313, Hi and H2 maintainmgthe axe of rotation of the cam followers at all times upon diametrically opposed sides of the cam, i. e, maintaining the cam fol.- lowers so positioned at all times that :a line connecting their axes of rotation will also pass through, or approximately through, the of rotation .of shaft I54 and cam s53. It will be clear that, as cam follower Hi) moves down- \vardly from its point of maximum height, which is when the sheave 22 is midway between the drum heads, the cam follower its will :be lifted through practically the same distance by the action v:of the swinging link I13 so that a line connecting the :axes'of the cam followers will always approximately pass through the axis of shaft I55. In the operation of the mechanism described there is little possibility of wear and accuracy of traverse of the cable guide 22 for long periods of time is assured. The mechanism is furthermore of great simplicity, and durable, essential features in :a balloon winch. The sheave 22 will, of course, oscillate during the paying out of the cable, as Welles during its winding in, and will serve to decrease wear of the cable which is caused by the rubbing of one convolution against the adjacent wrapping or convolution as the cable is unwound from the drum.

The shock absorber positioned intermediate the traction zdevice T and .the cable guide I3 has been previously referred to in general terms. It comprises :the sheave 15 and a spring mechanism generally indicated at :I-ll. The sheave is supported upon a bracket 18% in .such manner that it isflrotatable about an axis slightly inclined to the vertical. The bracket 118i] is pivotally connected at 1.815 and .182 to sleeve members Hand r84, respectively, these sleeve members being slidably mounted upon parallel, pivotally extending rods .1 and .1168 the ends of which aresupported in members It?! and I83 which are rigid with the frame of the winch. 'Encircling each of these guide rods are two helical compression springs one of relatively light resistance to compression, indicated at F915, and a second of considerably heavier resistance compression, indicated at I 9I the adjacent ends aligned springs abutting against an intennediate slidable division plate or washer member .192. I

It will be clear that, in-the event that the reach C of the cable, and hence :the reach 0 also, are placed in sudden and excessive'tension the sheave i5 with its supporting bracket and slides will be drawn to t'he left (Figures 1 and 3) this movement being opposed immediately by the lighter helical springs I and in asecondary manner by the heavier springs .l-z9I. If the sudden tension is not excessive the springs 19! will 'becompressed little if at all and the tension will be relieved by compression of the lighter springs I90 alone. Should the pull of the cable on the sheave 15 be of greater magnitude, however, the lighter springs I 98 will first be compressed practically to solid height, followed by-partial or full compression of the heavier springs I S I. l he shock relieving action of the mechanism just described will, of course, be entirely automatic. By reason of the inclinationof the axis of sheave IS a large sheave can be used at this point without making it-necessary to widely separate the guide rods I85 and I86 with their associated springs.

At the forward end of the winch a novel cable guide is employed, previously indicated in a general way by the numeral 13. The details of this cable guide may be most clearly perceived in Figures 24, 25, and'26 of the drawings. The guide I Figures 20, 21 and 22 and in these figures an inthe cross member 202 comprising a portion of the rigid frame of the winch. Each bracket 299 is provided with a pin or bolt 293, extending inwardlytoward sleeve I99 and entering an aperture formed in the sleeve for its reception; sleeve I99 being thus supported for rocking movement about a horizontal'axis coincident with aligned axes of the bolts or pivot pins 293. It may be moved about this axis from the position in which it is shown in full lines in the several figures of the drawings, which is its operative position, to the position in which it is shown in dotted lines in Figure 24, which is its inoperative position and the position which it is moved when the winch is to be transported.

To hold sleeve I99 firmly in position with its axis horizontal and the guide sheave I95 in its forward position, hold-down bolts 295 are provided, each of these bolts having its lower end pivotally connected to cars 296 rigid with the base 1 member 292' and being provided at its upper end with a threaded portion to receive a securing nut 29?. The undersurfaces of the securing nuts I91 ordinarily engage the horizontal upper surfaces of the parallel arms 208 extending outwardly from and rigid with the sleeve I99, thus holding down the forward end of the sleeve I99 despite any upward pull of the cable upon sheave I95.) In order to move the cable guide from its operative position to its inoperative position it will, of course, be necessary to first release nuts 20'! and swing thesebolts outwardly and downwardly so that the laterally extending arms 208 of the sleeve are disengaged. A weight 2m rigidly attached to the sheave supporting member normally tends to maintain the sheave I95 in a vertical plane but, in the usual case, the pull of the cable when the winch is in operation is the dominating factor and the sheave I95 will assume a position which is entirely dependent upon the horizontal angle between that reach of the cable which extends to the captive balloon and upon the vertical angle between this portion of the cable and the horizontal, the sheave being adapted to freely swing or revolve about the axis of the cylindrical portion I910 of the sheave support.

A guard to prevent escape of the cable from the groove in the sheave I95 is indicated at 2II, this guard comprising two side plates 2I2 provided with aligned apertures through which the pin I96 extends. The peripheral edges of the two side plates are connected a substantial angular distance around the axis of the guard, but not to such an extent as to interfere with the free movement of the cable into the sheave through the cable entry neck 2I3 or-the passage of the cable from the sheave I95, through the hollow interior of the cylindrical portion I9'Ic of the sheave support, on its way to guide sheave I'I. The casing 2H must, of course, be free to rotate about the axis of pin I96 as the angle ofthe cable with the vertical changes from time to time. The cable entry neck'2I3 is shown in detailv in sulating sleeve 2E5 is shown to', have a portion extending into and having threaded engagement with the inner surface of the neck. Encircling the outer end of this sleeve 2 I 5 of insulatingmaterial is a metallic contact member'ZIfi which is connected by a suitable helical conduit 2 IT to the ignition system of the prime mover I2. Mounted upon the cable C is a metallic disc 2 I 8 comprising two one-half portions secured together by screws M9 in such manner that the cable is securely gripped frictionally. The disc 2I8 is positioned on the cable at a point immediately below the captive balloon and, in the event that the operator neglects to stop the action of the traction device at the proper time when hauling in the balloon, the disc 2I9 will strike the contact member 2 I6 and thus cut out or ground the ignition system of the internal combustion engine which supplies the power for the operation of the winch, the cable C, of course, being grounded.

In the operation of a barrage balloon winch its operator must remain alert with upwardly directed gaze for long periods of time and it is essential that he be seated comfortably and in such manner that he can operate the winch controls with the least effort. also the winch must be compact and have relatively small overall dimensions when arranged for transportation. By the novel seat mechanism which is illustrated in Figures 16 to 19, inclusive,-

and providing a shifting canopy support, it is possible to meet the requirements in a most efiective manner,

The operators seat 229 is mounted upon a telescoping supporting leg 221, the seat being pivotally connected to the upper member 22 Id of the telescoping leg so that it may be rocked in a fore and aft direction from the position in which it is shown in dotted lines, a hand screw 222 of suitable type being provided to enable this adjustment to be quickly accomplished. The height of the seat above the winch frame may be adjusted by adjusting the telescoping supporting leg, the details of the means for securing the parts of the leg in different positions of adjustment, portion of which is indicated at 223, being relatively unimportant. The lower end of the supporting leg 22! is. slidably supported upon the frame for movement fore and aft of the winch and for rock- 7 ing movement laterally of the winch. A supporting rod 22d has its ends rigidly mounted in brackets 225 attached by bolts or the like to the adjacent side frame member of the winch. From the lower end of the supporting leg 22I parallel extensions 225 project downwardly upon opposite sides of the supporting rod 224-, these flange-like extensions being curved toward each other around the undersurfaces of the rod, as shown in Figure 1.9, and then projecting in parallelism for a fur: ther distance in a downward direction, these lowermost and parallel portions being provided with aligned apertures to receive a threaded bolt 22? provided with a nut 22B and a head 229 having wings by means of which it may be rotated. By the means just described the lower end of the supporting leg 22! may be securely clampedto the supporting rod 225 at any point along the length of the rod. The weight of the chair and occupant are transmitted to rodZZ I through antifriction rollers 22H). 7 s

Leg 22! is also provided at its lower end with means for bracing it transversely. This means comprises laterally'extending parallel webs 239 and EM, generally triangular in side elevation,

As previously explained,

provided with downwardly projecting hook-like portions the terminal end of one of which is indicated at 230a, these ends extending toward supporting rod 224 so as to comprise abutment members limiting the outward swinging movement of the web about this rod by contact with the undersurface of the upper horizontal flange of the main Winch side frame member, as clearly shown in Figure 19. Intermediate flanges 230 and 23B and supported for swinging movement upon a pivot 233 is a locking dog 234 which automatically falls into the full line position in which it is shown in Figures 17 and 19 when the seat post 22! is moved to a vertical position and which, by reason of the fact that its lower end bears upon the upper surface of the upper flange of the side frame member, prevents movement of the seat toward its dotted line position. The locking dog can be released, however, when it is desired to move the seat to an operative position, quickly and easily, the operator simply gripping the handle member 235 associated with the locking dog in applying the lifting force to this handle.

The protective canopy frame is indicated at 24 3 and is shaped as indicated in Figures 1 and 2 of the drawings, bein rectangular when viewed in plan, and a horizontal and an inclined portion when viewed from the side. Upon it may be placed any suitable protective shield for the winch operator. As shown in full lines in Figure 2 the canopy support is in its operative position and in order that it may occupy this position when the winch is in operation, and be moved inwardly so as not to project beyond the sides of the winch frame when the winch is to be transported, it is mounted for sliding movement upon parallel horizontal rods 24! and 242, these rods being in turn supported upon the upper ends of substantially vertical posts 24-3 and 244, respectively. Bearing members 245 and 246, at the opposite ends of the sliding canopy supporting frame 240 are rigid with this frame, but are slidable upon the horizontal supporting rods 24! and 242. By the means shown the canopy support 249 is permanently attached to the winch but may be readily adjusted laterally at any time.

Having thus described the invention, what is claimed as new and desired to be secured by Letters Patent is:

1. In a winch, in combination, a shaft supported for rotation about a fixed axis, a power driven element encircling the shaft, an overrunning clutch for transmitting driving torque from said element to said shaft, whereby the shaft will be positively driven in one direction of rotation by said element when said element is rotated about the axis of the shaft in one direction, a one-way brake for acting automatically to grip and hold said shaft against rotation in the direction opposite to that in which the shaft is rotated by the overrunning clutch, a drum mounted on the shaft for rotation relatively thereto in either direction, and means frictionally connecting the shaft and drum at all times.

2. In a winch, in combination, a shaft supported for rotation about a fixed axis, a power driven element encircling the shaft, an overrunning clutch for transmitting driving torque from said element to said shaft, whereby the shaft will be positively driven in one direction of rotation by said element when said element is rotated about the axis of the shaft in one direction, a one-way brake for acting automatically to grip 18 and hold said shaft against rotation in the direction opposite to that in which the shaft is rotated by the overrunning clutch, a drum mounted on the shaft for rotation relatively thereto in either direction, and means frictionally connecting the shaft and drum at all times, said means including a disc mounted on the shaft, annular friction surfaces carried by the drum and disposed concentrically to the axis of the shaft, the outer margin of the disc being intermediate the said friction surfaces, and resilient elements normally urging said friction surfaces toward each other to clamp said disc.

3. In a winch, in combination, a shaft supported for rotation about a fixed axis, a power driven element encircling the shaft, an overrunning clutch for transmitting driving torque from said element to said shaft, whereby the shaft will be positively driven in one direction of rotation by said element when said element is rotated about the axis of the shaft in one direction, a one-way brake for acting automatically to grip and hold said shaft against rotation in the direction opposite to that in which the shaft is rotated by the overrunning clutch, a drum mounted on the shaft for rotation relatively thereto in either direction, and means frictionally connecting the shaft and drum at all times, said means including a disc mounted on the shaft, annular friction surfaces carried by the drum and disposed concentrically to the axis of the shaft, the outer margin of the disc being intermediate the said friction surfaces, a series of springs disposed in a circular series about said shaft, for normally urging said friction surfaces toward each other, and means for simultaneously adjusting the action of said springs.

4. The combination set forth in claim 1 in which the outer member of the torque transmitting clutch comprises a sleeve upon which a driving sprocket is fixed, said sleeve enclosing a sprocket supporting bearing,

5. The combination set forth in claim 1 in which the overrunning clutch and the one-way brake are disposed respectively at the extreme ends of the shaft, and each comprises inner and outer members, portions of said respective inner and outer members comprising cooperating portions of supporting bearings, the one for supporting the said power driven element from the shaft, and the other for supporting the shaft from a relatively stationary part of the winch.

, JOHN HART WILSON.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS 

